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EP0971160B1 - Robinet-vanne commandé pour un compresseur à piston - Google Patents

Robinet-vanne commandé pour un compresseur à piston Download PDF

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Publication number
EP0971160B1
EP0971160B1 EP19990810495 EP99810495A EP0971160B1 EP 0971160 B1 EP0971160 B1 EP 0971160B1 EP 19990810495 EP19990810495 EP 19990810495 EP 99810495 A EP99810495 A EP 99810495A EP 0971160 B1 EP0971160 B1 EP 0971160B1
Authority
EP
European Patent Office
Prior art keywords
valve
plate
accordance
counter
valve plate
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Expired - Lifetime
Application number
EP19990810495
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German (de)
English (en)
Other versions
EP0971160A1 (fr
Inventor
Cyrill Steinebrunner
Erich Kläui
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Burckhardt Compression AG
Original Assignee
Burckhardt Compression AG
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Burckhardt Compression AG filed Critical Burckhardt Compression AG
Priority to EP19990810495 priority Critical patent/EP0971160B1/fr
Publication of EP0971160A1 publication Critical patent/EP0971160A1/fr
Application granted granted Critical
Publication of EP0971160B1 publication Critical patent/EP0971160B1/fr
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
    • F16K3/00—Gate valves or sliding valves, i.e. cut-off apparatus with closing members having a sliding movement along the seat for opening and closing
    • F16K3/02—Gate valves or sliding valves, i.e. cut-off apparatus with closing members having a sliding movement along the seat for opening and closing with flat sealing faces; Packings therefor
    • F16K3/04—Gate valves or sliding valves, i.e. cut-off apparatus with closing members having a sliding movement along the seat for opening and closing with flat sealing faces; Packings therefor with pivoted closure members
    • F16K3/06—Gate valves or sliding valves, i.e. cut-off apparatus with closing members having a sliding movement along the seat for opening and closing with flat sealing faces; Packings therefor with pivoted closure members in the form of closure plates arranged between supply and discharge passages
    • F16K3/08—Gate valves or sliding valves, i.e. cut-off apparatus with closing members having a sliding movement along the seat for opening and closing with flat sealing faces; Packings therefor with pivoted closure members in the form of closure plates arranged between supply and discharge passages with circular plates rotatable around their centres
    • F16K3/085—Gate valves or sliding valves, i.e. cut-off apparatus with closing members having a sliding movement along the seat for opening and closing with flat sealing faces; Packings therefor with pivoted closure members in the form of closure plates arranged between supply and discharge passages with circular plates rotatable around their centres the axis of supply passage and the axis of discharge passage being coaxial and parallel to the axis of rotation of the plates
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B39/00—Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00
    • F04B39/08—Actuation of distribution members
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
    • F16K31/00—Actuating devices; Operating means; Releasing devices
    • F16K31/02—Actuating devices; Operating means; Releasing devices electric; magnetic
    • F16K31/04—Actuating devices; Operating means; Releasing devices electric; magnetic using a motor
    • F16K31/041—Actuating devices; Operating means; Releasing devices electric; magnetic using a motor for rotating valves

Definitions

  • the invention relates to an actively controlled valve for a reciprocating compressor according to the preamble of independent claim 1.
  • the invention further relates to a method for the externally controlled actuation of a Kolbenkompressorventits by its own drive mechanism according to the preamble of independent Claim 18.
  • the suction and discharge valves of reciprocating compressors are today mostly as spring-loaded, self-medium actuated valves, for example as Plate valves, designed.
  • a plate valve typically includes a plate-shaped valve seat, a valve plate and a plate-shaped Valve catcher, seen in the axial direction of the valve one behind the other are arranged and held together by a central screw.
  • the valve plate is between the valve seat and the valve catcher arranged and acting through between valve catcher and valve plate Springs are biased against the valve seat so that they pass through the passages Closes valve seat sealingly.
  • the valve plate against the force of the springs in the axial Direction lifted from the valve seat and gives the passage for the medium free. If the pressure of the own medium falls below the closing pressure, then The springs press the valve plate against the valve seat and the Valve closes.
  • valves are thus actuated passively, that is, the movement of the Valve plate or similar valve body results essentially from the Ratio of forces generated by the intrinsic medium, the springs and the Caused masses.
  • One of the main problems of such valves is their unsatisfactory valve kinematics. They open and close slowly; of the Opening or closing time related to the working cycle of the Piston compressor can be adjusted only inaccurate and not optimal. For example, if relatively weak springs used, so is the hub Although the valve plate enough large enough to a sufficient To realize flow cross-section of the valve, but the valve usually closes too late or too slowly. If you choose stronger, on the other hand Springs, so the valve closes faster, but the stroke of the valve plate is significantly lower, resulting in an adverse reduction of Flow cross-section results.
  • valves tend to flow-excited vibrations, which also be referred to as aeroelastic flutter.
  • the valve plate bounces often back at the end stop.
  • the prior art active valves z. B. mushroom valves Car engines, known, that is, such valves by their own Drive mechanism operated externally controlled.
  • the operation such active valves for example via a cam drive and appropriately designed transmission linkage, which the Control stroke movement of the valve plate relative to the valve seat.
  • Actively controlled Plate valves have the advantage that the flowing medium no Energy must be removed to operate the valve.
  • the actively controlled valve that accomplishes these tasks is characterized by the features of independent claim 1.
  • an actively controlled valve for a Piston compressor proposed that a valve plate and a Counter plate comprises, which have both passage openings, wherein the Valve plate is mounted such that it is about the longitudinal axis of the valve and is rotatable relative to the counter-plate, and wherein the valve has a means to move the valve plate, in the longitudinal axis of the valve.
  • the valve further comprises a drive device connected to the valve plate, to rotate the valve plate relative to the backing plate.
  • the object is further achieved by a method for active driving a piston compressor valve comprising the features of claim 18.
  • valve plate and the counterplate oriented relative to each other such that the Passage openings in the counter plate closed by the valve plate become.
  • valve plate is a predetermined Angle relative to the backing plate and rotated about the longitudinal axis of the valve, so that the passage openings in the valve plate on the Passage openings in the counter plate come to rest. In this way creates a continuous flow cross-section for the medium, that is, the valve is in its open position.
  • Valve plate also by a predetermined angle about the longitudinal axis of Valve turned so that they the passage openings in the back plate closes tightly.
  • the Drive device preferably an electric drive with a stator and a rotor, wherein the rotor rotatably connected to the valve plate is.
  • This drive is an easy way to represent the angular position of Valve plate relative to the backing plate quickly and with sufficient precision to control.
  • the runner is preferred as a low-mass runner, especially as tubular runner, designed.
  • Valve means provided to the valve plate relative to To move counter plate in the axial direction.
  • To open and close of the valve performs the valve plate from a combined stroke-rotation movement.
  • the amplitude of the stroke is comparatively low, for Example only about 0.1 mm.
  • the valve plate can substantially frictionless relative to the backing plate to be twisted. This makes it practical no wear of valve and counter plate, so a very long Life of the valve is guaranteed.
  • the means for moving the valve plate in the axial direction can one Solenoid comprise, which is arranged so that it is an axially directed Force on the valve plate and / or the runner can exercise. It is too possible to design the electric drive so that it has an axial directed force can exert on the valve plate.
  • the counter-plate, the valve plate and the rotor along a support element extending in the axial direction arranged, wherein the storage of the valve plate and the rotor with respect the wearer wear-free, in particular frictionless, designed is.
  • this wear-free storage realized by the fact that the valve plate and the rotor by means of bending springs are connected to the carrier element.
  • the spiral springs extend in radial direction between the carrier element on the one hand and the Valve plate or the runner on the other.
  • the bending springs become elastic deformed. Due to the bending springs, the valve plate or the runner is also mounted movable and wear-free with respect to the axial direction, so that any additional minor Lifting movement of the valve plate in the axial direction is also possible.
  • the rotor magnetic and non-contact to store with respect to the support element.
  • Fig. 1 shows a longitudinal sectional view of the essential parts of a Embodiment of the actively controlled valve according to the invention, which is designated overall by the reference numeral 1.
  • the valve 1 is in housed a valve housing, not shown. That in Fig. 1 illustrated embodiment is as a pressure valve for a Reciprocating compressor designed. It is understood that that according to the invention, actively controlled valve 1 in a similar manner can also be configured as a suction valve.
  • the active valve 1 comprises a valve plate 2, which in Fig. 3 in a plan view is shown, as well as a counter plate 3. Both in the valve plate 2 as also in the counter-plate 3 each have a plurality of passage openings 21 and 31 is provided, which preferably each as a radially extending slots are formed, which seen in the circumferential direction equidistantly over the Valve plate 2 and the counter-plate 3 are distributed as shown in FIG. 3 shows. The Dimensions of the slots and their mutual distance are on the Valve plate 2 the same as on the counter plate. 3
  • the counter-plate 3 is rigid with a rod-shaped support element. 9 connected in the axial direction, indicating the direction of the longitudinal axis A of the valve 1 is meant extends. In normal operating condition this is Carrier element 9 and thus also the counter-plate 3 fixed relative to the Compressor housing arranged. In the assembled state, the Counter plate 3 z. B. in a conventional manner in the housing of the Compressor and thus carries the valve 1. The valve 1 is so mounted that the compression space of the compressor according to the representation (FIG. 1) located below the counter-plate 3.
  • valve plate 2 is in the axial direction adjacent to the counter-plate 3, according to the representation above this, arranged. In the closed position of the Valve 1, the valve plate 2 is sealingly on the counter plate 3 and is supported by this.
  • the valve plate 2 is in the embodiment described here by means of Bending springs 11 rotatable and axially movable with respect to the support member. 9 stored.
  • the valve plate 2 is configured annular, that is, it has a central opening 22 in the axial direction. Through this central opening 22 extends the support member 9.
  • the support member 9 is over several Bending springs 11 with the radially inner boundary surface of the Valve plate 2 is connected, wherein the bending springs 11 each arranged so are that they run in their rest position in the radial direction.
  • the Valve plate 2 mounted so that it is about the longitudinal axis A of the valve. 1 and is rotatable relative to the counter-plate 3.
  • valve plate 2 is the second with respect to the counter-plate 3 oriented such that the areas between the passage openings 21 in the valve plate 2 as shown the passage openings 31 are in the counter-plate 3, so that the latter be covered by the valve plate 2.
  • the valve plate 2 is located sealing on the back plate 3 and there is no continuous Flow connection through the valve 1.
  • the Valve plate 2 is closed by a predetermined angle, which essentially by the Expansion of a passage opening 21, 31 is fixed in the circumferential direction, rotated about the longitudinal axis A of the valve 1, so that the passage openings 31,21 in the counter-plate 3 and in the valve plate 2 to coincide. Now there is a continuous flow connection.
  • the inventive active valve is by means of a drive device 4th externally controlled.
  • the Drive device an electric drive 4, which is not a represented control and supply unit is powered and is controlled.
  • the control takes place z. B. depending on Clock of the piston movement of the compressor.
  • the electric drive comprises in a coaxial arrangement, a stator 7 with windings 71, a rotor 6 and a yoke 5 whose common axis is the longitudinal axis A of Valve 1 is.
  • Fig. 2 shows a Cross section through the embodiment along the section line II-II in Fig. 1.
  • the stator 7 arranged on the inside and arranged on the carrier element 9.
  • the Stator 7 is of a sleeve-shaped, external yoke 5 for Surround the magnetic field, which is also arranged on the carrier element 9 is.
  • the rotor 6 of the electric drive 4 arranged as a tubular Runner 6 is formed.
  • the rotor 6 is low in mass, so that in the Acceleration of the rotor 6 only small inertial forces occur. from that results in the advantage that the valve 1 operates very fast, ie within a very short time can be opened or closed.
  • the tubular rotor 6 is at its one end (with respect to the axial Direction) directly and rotatably connected to the valve plate 2, so that this forms an axial end face of the rotor 6.
  • a annular disc-shaped part 61 which is the second axial Begrenzugs Stretor 6 forms and within the inference 5 on the Carrier element 9 is mounted.
  • the storage of the annular disc-shaped part 61 on the support member 9 is in an analogous manner as the front for the Valve plate 2 explained by means of bending springs 11 realized so that the entire Unit of rotor 6 and valve plate 2 rotatable and axially movable on the Carrier element 9 is mounted.
  • the Biegefedem 11 are arranged so that the valve. 1 is open when the bending springs in their resting or equilibrium position are. This results in the advantage that the valve 1 in case of failure of the Electric drive 4 opens automatically and no unacceptably high pressure arises in the compressor.
  • Valve 1 means to the valve plate 2 relative to the counter-plate 3 in the axial To move direction.
  • opening or closing the valve 1 leads the Valve plate then, as will be explained later, a combined stroke-rotation movement from which the advantage results that practically no Wear on the back plate 3 and the valve plate 2 by the operation of the valve 3 occurs because the rotational movement can be done without friction.
  • the means for Moving the valve plate 2 in the axial direction of an annular Solenoid 10, which is designed as an electromagnet and also from the not shown control and supply unit is controlled.
  • the Solenoid 10 is arranged in the axial end face of the yoke 5, so that it is opposite to the annular disk-shaped part 61 of the rotor 6.
  • this exerts an axially directed force on the rotor 6 and thus on the valve plate 2, so that the latter of the Counter plate 3 is lifted.
  • valve 1 functions as follows: If the valve 1 is in its open position, then, as already at the front explained, the valve plate 2 with respect to the counter-plate 3 oriented such that the passage openings 31 in the counter-plate 3 and the passage openings 21 superimposed in the valve plate 2, so that the medium is the valve. 1 can flow through.
  • the solenoid 10 activates the Control and supply unit first, the solenoid 10, then the Runner 6 in the axial direction and thus attracts the runner. 6 connected valve plate 2 lifts from the back plate 3. At this Movement, the bending springs 11 are elastic in the axial direction deformed.
  • the lifting movement typically has only a very minor one Amplitude of, for example, 0.1 mm.
  • Valve plate 2 is separated from the base plate 3, so that the subsequent Rotational movement can be carried out without glide and friction.
  • controls the control and Supply unit to the electric drive 4 such that the rotor. 6 and thus the valve plate 2 by a predetermined angle to the Support member 9 is rotated, wherein the angle is dimensioned so that after rotation, the areas between the passage openings 21 in the Valve plate 2 via the passage openings 31 in the counter plate. 3 are located.
  • the bending springs 11 in the Circumferentially deformed elastically.
  • valve plate 2 settles, supported by the resetting Force of the bending springs 11 in the axial direction, on the counter-plate 3, whose Through openings 31 are thereby sealed.
  • the valve 1 is closed.
  • the valve plate 2 is again initially raised in the axial direction by means of the lifting magnet 10, then at the same angle as when closing, but in opposite direction, rotated and then in the axial direction lowered so that it rests again on the counter plate 3, but in one such orientation that the passage openings in the counter-plate 3 and lie one above the other in the valve plate 2.
  • the rotor 6 can act as an asynchronous squirrel-cage rotor made of conductive material slotted or unslotted be formed as a synchronous or stepper motor rotor with Permanent magnet or as reluctance rotor, which is a ferromagnetic Material includes.
  • the rotor 6 is preferably made of a lightweight material. So is for example, in the case of a squirrel cage, aluminum is a preferred one Material.
  • the electric drive 4 can of course also with internal Runners 6 may be formed, for example by the in Fig. 1 and Fig. 2 shown arrangement of stator 7 and yoke 5 is reversed.
  • the formation of the storage of the valve plate 2 and the rotor 6 with respect the support member 9 by means of the bending springs 11 has the advantage that this Bearing clearance, wear-free, and friction-free, in particular is friction-free. From the play-free storage results in a high Precision in the operation of the valve 1, so a safe and reliable operation is ensured.
  • the frictionless and wear-free Storage of the movable valve components, namely the rotor 6 and the valve plate 2 leads to a very long life.
  • the active valve is practical wear-free.
  • the active actuation of the inventive valve 1 makes it possible to Opening and closing times in each case optimal and in particular regardless of the pressure exerted by the medium. This has the advantage that significantly lower energy losses occur, thereby the efficiency of the valve 1 improves. Furthermore, the Regulate the performance of the compressor in a very simple way. That's the way it is For example, by the external control possible, the pressure valve during one or more working cycles to be kept open at all times so as to easy to adjust the capacity of the compressor as needed to reduce. If z. B. the pressure valve during every fourth cycle left in the open position, so the performance of the compressor to reduced by about 25%.
  • valve 1 with the electric drive 4 which has a low-mass, especially a tubular, rotor 6 leads to a very fast valve, that is the release or blocking of the Flow cross-section through the valve 1 can be done in a very short time, because the masses to be moved during actuation are small and thus only small inertial forces occur.
  • This is especially with regard to very powerful compressors a big advantage, because in known The opening and closing times are often an important factor represent the maximum achievable working speed (Piston speed) of the compressor limited.
  • the Means for moving the valve plate 2 in the axial direction in the be integrated electric drive.
  • the electric drive 4 is then designed such, for example, by a corresponding arrangement and Driving the windings 71 of the stator 7, that he in addition to the Torque an axially directed force on the rotor 6 and with him connected valve plate 2 can exercise.
  • the bending springs 11 may be configured differently, for. B. in such a way that, in the rest position, it spirals between the rotor 6 or the valve plate 2 and the support member 9 extend.
  • the rotor 6 magnetic and Store without contact with respect to the support member 9.
  • the storage of Unit from the rotor 6 and the valve plate 2 then takes place by means of itself known magnetic bearing, z. B. by means of radial bearings, the rotor 6 with respect Keep the longitudinal axis A of the valve centered.
  • Mitttel for the magnetic bearing in the electric drive 4 too integrate, for example by an appropriate design and Arrangement of the windings 71 of the stator 7, so that the electric drive can both exert a torque on the rotor 6 and the runner magnetic and non-contact with respect to the longitudinal axis A of the valve centered stores.
  • the non-contact magnetic bearing of the rotor 6 with respect to Carrier element 9 brings the already mentioned advantage that they is friction and wear-free.
  • the valve plate 2 when opening and closing the valve. 1 each in the same direction to turn.
  • inventive valve 1 in addition to a Damper plate between the valve plate 2 and the back plate 3 is provided can be, for. B. in accordance with the same manner as that of conventional Plate valves is known.
  • the valve 1 according to the invention is characterized in particular by that no bouncing and no flutter of the valve plate 2 occurs, whereby a Material fatigue is counteracted, so that the valve 1 in Operating state has a very long life.
  • the inventive valve allows excellent valve kinematics with short opening and closing times as well as optimally adjustable Opening and closing times. Furthermore, the inventive Valve are designed virtually wear-free.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Sliding Valves (AREA)
  • Magnetically Actuated Valves (AREA)

Claims (25)

  1. Vanne commandée activement pour un compresseur à piston, comprenant une plaque de vanne (2) et une contre-plaque (3), qui présentent toutes les deux des ouvertures traversantes (21, 31), où la plaque de vanne (2) est logée de façon à pouvoir tourner autour de l'axe longitudinal (A) de la vanne et relativement à la contre-plaque (3), et comprenant un dispositif d'entraínement (4) pour entraíner la plaque de vanne (2) afin de faire tourner celle-ci relativement à la contre-plaque (3), caractérisée en ce qu'il est prévu additionnellement un moyen pour déplacer la plaque de vanne (2) relativement à la contre-plaque (3) également dans la direction de l'axe longitudinal (A).
  2. Vanne selon la revendication 1, où le dispositif d'entraínement est un entraínement électrique (4) avec un stator (7) et un rotor (6), où le rotor (6) est relié d'une manière non tournante à la plaque de vanne (2).
  3. Vanne selon la revendication 2, où le rotor (6) est réalisé comme rotor (6) pauvre en masse, en particulier comme rotor tubulaire (6).
  4. Vanne selon l'une des revendications précédentes, caractérisée en ce que la course en direction de l'axe longitudinal (A) est de 0,1 mm.
  5. Vanne selon l'une des revendications précédentes, où le moyen de déplacement de la plaque de vanne (2) dans la direction longitudinale (A) comprend un aimant de levage (10) qui est disposé de façon qu'il puisse exercer une force dirigée axialement sur la plaque de vanne (2) et/ou le rotor (6).
  6. Vanne selon l'une des revendications 2 à 5, où le moyen de déplacement de la plaque de vanne (2) dans la direction longitudinale (A) est intégré dans l'entraínement électrique (4) et que ce dernier est donc réalisé de façon qu'il puisse exercer une force dirigée axialement sur le rotor (6).
  7. Vanne selon l'une des revendications précédentes, caractérisée en ce que le dispositif d'entraínement (4) et le moyen de déplacement de la plaque de vanne (2) peuvent être commandés en direction de l'axe longitudinal (A) de façon que la plaque de vanne (2), pour ouvrir et/ou fermer la vanne (1), exécute un mouvement de levage et de rotation combiné.
  8. Vanne selon l'une des revendications 2 à 7, où la contre-plaque (3), la plaque de vanne (2) et le rotor (6) sont disposés le long d'un élément de support (9) s'étendant dans la direction axiale, où le logement de la plaque de vanne (2) et du rotor (6) par rapport à l'élément de support (9) est réalisé sans usure, en particulier sans frottement.
  9. Vanne selon la revendication 8, où le rotor (6) est logé de manière magnétique et sans contact relativement à l'élément de support (9).
  10. Vanne selon la revendication 8, où la plaque de vanne (2) et le rotor (6) sont reliés par des ressorts de flexion (11) à l'élément de support (9).
  11. Vanne selon la revendication 10, caractérisée en ce que les ressorts de flexion (11) sont disposés de façon que ceux-ci, lorsque la vanne (1) est ouverte, se trouvent en position de repos.
  12. Vanne selon l'une des revendications précédentes, réalisée comme une vanne de pression ou une vanne d'aspiration.
  13. Vanne selon l'une des revendications précédentes, caractérisée en ce que les ouvertures traversantes (21, 31) sont réalisées comme des fentes s'étendant radialement, qui sont réparties dans la direction périphérique d'une manière équidistante sur la plaque de vanne (2) respectivement la contre-plaque (3).
  14. Vanne selon la revendication 13, caractérisée en ce que les dimensions des fentes et leur écart mutuel sur la plaque de vanne (2) sont identiques à ceux de la contre-plaque (3).
  15. Vanne selon la revendication. 13 ou 14, caractérisée en ce que la dimension des fentes est réalisée de façon qu'un angle de rotation entre la plaque de vanne (2) et la contre-plaque (3) inférieur à 45° est requis pour ouvrir respectivement fermer les ouvertures traversantes (21, 31).
  16. Vanne selon l'une des revendications précédentes, caractérisée en ce qu'une plaque d'amortissement est disposée entre la plaque de vanne (2) et la contre-plaque (3).
  17. Compresseur à piston avec une vanne (1) qui est réalisée selon l'une des revendications précédentes.
  18. Procédé pour l'actionnement piloté d'une vanne de compresseur à piston (1) par un mécanisme d'entraínement propre, où la vanne (1) comprend une plaque de vanne (2) et une contre-plaque (3), et où la plaque de vanne (2) est logée de façon que celle-ci puisse tourner et être entraínée autour de l'axe longitudinal (A) de la vanne et relativement à la contre-plaque (3), et où la plaque de vanne (2) et la contre-plaque (3) sont tournées selon une telle alternance entre deux états, une position de fermeture et une position d'ouverture, que la vanne (1) se trouve soit dans une position de fermeture, dans laquelle les ouvertures traversantes (31) de la contre-plaque (3) sont fermées par la plaque de vanne (2), ou que la vanne (1) se trouve dans une position d'ouverture, dans laquelle la plaque de vanne (2) se situe de telle sorte au-dessus de la contre-plaque (3) qu'il se produit une section transversale d'écoulement traversante, caractérisé en ce que la plaque de vanne (2), lors de l'ouverture et de la fermeture de la vanne (1), est également déplacée en direction de l'axe longitudinal (A) et, ce faisant, exécute un mouvement de levage et de rotation combiné.
  19. Procédé selon la revendication 18, caractérisé en ce qu'avant le mouvement de rotation, le mouvement de levage est exécuté, en ce que la plaque de vanne (2) est déplacée selon l'axe longitudinal (A) et est relevée de ce fait de la plaque de base (3).
  20. Procédé selon la revendication 18 ou 19, caractérisé en ce que la plaque de vanne (2), lors de l'ouverture et de la fermeture de la vanne (1), est tournée respectivement dans la même direction.
  21. Procédé selon l'une des revendications 18 à 20, caractérisé en ce que la plaque de vanne (2) est amenée par une rotation inférieure à 45° de la position de fermeture dans la position d'ouverture ou bien de la position d'ouverture dans la position de fermeture.
  22. Procédé de commande du débit d'un compresseur à piston avec une vanne commandée selon l'une des revendications 18 à 21.
  23. Procédé selon la revendication 22, caractérisé en ce que la vanne (1), pendant un ou plusieurs cycles de travail du compresseur à piston, reste en permanence dans la position d'ouverture.
  24. Procédé selon la revendication 22 ou 23, caractérisé en ce que l'instant d'ouverture et l'instant de fermeture de la vanne (1) sont commandés indépendamment de la pression du milieu.
  25. Compresseur à piston avec une vanne (1), qui est réalisée selon l'une des revendications 1 à 16, amenée à fonctionner avec un procédé selon l'une des revendications 22 à 24.
EP19990810495 1998-07-07 1999-06-07 Robinet-vanne commandé pour un compresseur à piston Expired - Lifetime EP0971160B1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
EP19990810495 EP0971160B1 (fr) 1998-07-07 1999-06-07 Robinet-vanne commandé pour un compresseur à piston

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
EP98810640 1998-07-07
EP98810640 1998-07-07
EP19990810495 EP0971160B1 (fr) 1998-07-07 1999-06-07 Robinet-vanne commandé pour un compresseur à piston

Publications (2)

Publication Number Publication Date
EP0971160A1 EP0971160A1 (fr) 2000-01-12
EP0971160B1 true EP0971160B1 (fr) 2005-04-13

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EP19990810495 Expired - Lifetime EP0971160B1 (fr) 1998-07-07 1999-06-07 Robinet-vanne commandé pour un compresseur à piston

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Cited By (1)

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WO2009050215A2 (fr) 2007-10-18 2009-04-23 Burckhardt Compression Ag Soupape à commande active, et procédé pour faire fonctionner une soupape à commande active

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IT1314504B1 (it) 2000-03-02 2002-12-18 Cozzani Mario S R L Valvola per il controllo di flussi di grande sezione, in particolareper compressori o simili.
US20030037817A1 (en) * 2001-08-21 2003-02-27 Fmc Technologies, Inc High-speed water jet blocker
ITCO20110072A1 (it) * 2011-12-22 2013-06-23 Nuovo Pignone Spa Valvole con elemento di chiusura valvolare collegato alla contro-sede attuata e relativi metodi
US8974201B2 (en) * 2012-02-23 2015-03-10 Ge Oil & Gas Compression Systems, Llc Rotating compressor valve
CN110651122B (zh) * 2017-03-27 2021-05-11 伯克哈特压缩机股份公司 活塞压缩机阀和活塞压缩机阀操作方法
JP7165670B6 (ja) 2017-03-27 2023-08-18 ブルクハルト コンプレッション アーゲー ピストンコンプレッサバルブ用のバルブクロージャおよびそのバルブクロージャを動作させるための方法

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US5345968A (en) * 1993-03-24 1994-09-13 General Electric Company Rotary magnetic valve for low noise low wear operation
US5417083A (en) * 1993-09-24 1995-05-23 American Standard Inc. In-line incremetally adjustable electronic expansion valve
GB2285303B (en) * 1993-12-31 1997-07-23 Hwang Shao Keh Magnetic control-type flow control valve
KR19990063951A (ko) * 1995-10-03 1999-07-26 후버 페. 플레이트형 구조로 된 흡기밸브의 제조방법 및 장치

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2009050215A2 (fr) 2007-10-18 2009-04-23 Burckhardt Compression Ag Soupape à commande active, et procédé pour faire fonctionner une soupape à commande active
WO2009050215A3 (fr) * 2007-10-18 2009-07-23 Burckhardt Compression Ag Soupape à commande active, et procédé pour faire fonctionner une soupape à commande active

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